US3777580A - Motion and force transforming mechanism - Google Patents

Motion and force transforming mechanism Download PDF

Info

Publication number
US3777580A
US3777580A US00185273A US3777580DA US3777580A US 3777580 A US3777580 A US 3777580A US 00185273 A US00185273 A US 00185273A US 3777580D A US3777580D A US 3777580DA US 3777580 A US3777580 A US 3777580A
Authority
US
United States
Prior art keywords
input
output
motion
gear
wheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00185273A
Other languages
English (en)
Inventor
J Brems
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3777580A publication Critical patent/US3777580A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18088—Rack and pinion type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18992—Reciprocating to reciprocating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/1967—Rack and pinion

Definitions

  • ABSTRACT A self-contained motion and force transmitting mechanism which includes a housing having a straightline input member and a straight line output member with included mechanism to translate a constant velocity input to a desired acceleration and deceleration output with a desired constant velocity interposed between the ends of the stroke.
  • the package mechanism described herein in one of its versions, can be applied in all of these situations, and will result in better and more predictable performance at lesser expense.
  • the device may be used as a stroke converter, for welding machines, piercing devices, press feeders, shock absorbers and internal snubbers and numerous other applications.
  • One example might be an application in which a given movement requires relatively little force over the first nine-tenths of its stroke, but requires a great deal of force to complete the remaining one-tenth of its stroke.
  • Another example might be an application in which it is required to convert an essentially constant velocity into an approximate sawtooth velocity, i.e., a velocity which builds up slowly at an approximate constant rate, then abruptly decreases to zero.
  • a third example might be an application in which it is desired to accomplish a movement with a short steep acceleration at the beginning of the stroke, a relatively low acceleration and deceleration during the middle range of the stroke, and finally a short steep deceleration at the end of the stroke, with the added condition that the acceration start from zero.
  • FIGS. 8 to M an isometric assembly view of a modified device and six relevant sections A-A, B-B,
  • FIGS. to 19 five sequential movement schematic drawings for a slide mode in-phase system.
  • FIG. 31 a kinematic line drawing for a slide mode, straight rack, out-of-phase system.
  • FIG. 32 a kinematic line drawing for a link mode, straight rack, in-phase system.
  • FIG. 33 a kinematic line drawing for a link mode, straight rack, out-of-phase system.
  • FIG. 34 a kinematic line drawing for a slide mode, curved rack, outof-phase system.
  • FIG. 35 a kinematic line drawing for an inclined slide, straight rack, out-of-phase system.
  • FIG. 36 a set of illustrative characteristic curves which relate output displacement to input displacement for a slide mode, straight rack, in-phase system.
  • FIG. 37 a set of illustrative characteristic curves which relate output relative velocity to input displacement for a slide mode, straight rack, in-phase system.
  • FIG. 38 a set of illustrative characteristic curves which relate output relative acceleration to input displacement for a slide mode, straight rack in-phase system.
  • FIG. 39 another set of curves as in FIG. 36 but with different output parameters R
  • FIG. 40 another set of curves as in FIG. 37 but with different output parameters R,.
  • FIG. 41 another set of curves as in FIG. 38 but with different output parameters R
  • FIG. 42 a set of illustrative characteristic curves which relate output displacement to input displacement for a slide mode, straight rack, out-of-phase systern.
  • FIG. 43 a set of illustrative characteristic curves which relate output relative velocity to input displacement for a slide mode, straight rack, out-of-phase system.
  • FIG. 44 a set of illustrative characteristic curves which relate output relative acceleration to input displacement for a slide mode, straight rack, out-of-phase system.
  • FIG. 45 a set of illustrative characteristic curves which relate output relative velocity to input displacement for a link mode, straight rack, out-of-phase and in-phase system.
  • FIG. 46 another set of curves as in FIG. 45, but with a different value of input parameter R
  • FIG. 47 a set of illustrative characteristic curves which relate output relative velocity to input displacement for a slide mode, curved rack in-phase system.
  • FIG. 48 a section drawing comparable to FIGS. 6 and 13 showing the construction of the mechanism with a cylindrical rather than rectangular section case or housing.
  • the device may be built in a variety of mechanical arrangements, the most important of which are shown and described in detail.
  • the basic frame which comprises the case or housing 18 of the mechanical assembly consists of seven members: an input end plate 20, an output end plate 26, a lower case plate 32, an upper case plate 34, two side case plates 36, and a rack 38 mounted on the longitudinal centerline of case plate 32, FIG. 3.
  • the four case plates are each bolted to the input plate 20 and the output plate 26.
  • adjacent case plates are bolted to each other to form a rigid box housing suitable for accepting and transmitting the internal loads to an external mounting surface.
  • An input rod 40 extends through the input head 20 and is supported therein through bushing 22.
  • a sea] 24 is provided to keep lubricants in and dirt out.
  • This input rod is further guided by crosshead 42, which in turn is guided by the upper case plate 34, the lower case plate 32, and the two side case plates 36.
  • a pin 44 extends through the crosshead 42 and connects two coupler links 48 thereto through bearings 46.
  • the other ends of the coupler links 48 are connected to eccentrics 50 through bearings 52.
  • the eccentrics 50 are rigidly bolted to or integral with gear 54.
  • the eccentricity of the eccentrics 50 from the true centerline of the gear 54 may be varied from 0 (concentric) to slightly more than the pitch radius of the gear, as one of the parameters which controls the force and kinematic characteristics of the system.
  • An output rod extends through the output head plate 26 and is supported therein through bearings 28.
  • a seal 30 is again provided to keep the lubricants in and the dirt out.
  • This output rod is further guided by crosshead 72, which in turn is guided by the upper case plate 34, the lower case plate 32, and the two side case plates 36.
  • a pin 74 extends through the crosshead 72 and connects one end of two connector links 78 thereto through bearings 76.
  • the other ends of the connector links 78 are connected to eccentrics 80 through bearings 82.
  • the eccentrics 80 are rigidly bolted to or integral with the adjacent eccentrics 50.
  • the eccentricity of the output eccentrics 80 may be varied from the true centerline of a drive wheel in the form of a gear 54 to slightly more than the pitch radius of the gear as another of the parameters which control the force and kinematic characteristics of the system.
  • the centerlines of the eccentrics 50 and 80 are shown as lying on the same radial line drawn from the gear 54 center.
  • a rack 38 is rigidly bolted to the lower case plate 32 and is suitably formed and located to mesh with the gear 54.
  • the gear teeth are conventional and not shown.
  • This rack 38 will generally but not necessarily be slightly longer than one pitch circumference of the gear 54.
  • the gear 54 is provided with shoulders 55 which operate in bearings 58 mounted in guide block 56.
  • This guide block 56 in turn is also guided between the lower case plate 32 and the upper case plate 34, and maintains the pitch line of the gear 54 on the pitch line of the rack 38 during the rolling of the gear 54 along the rack 38.
  • This mechanism is defined to be operating in the link mode because the centers of the eccentrics are link connected to their respective crossheads by pivot connected links.
  • the slide mode mechanism is described below.
  • the basic frame which comprises the housing of the mechanical assembly consists of seven members: an input end plate 20, an output end plate as, a lower case plate 32, an upper case plate 3d, two side case plates 36 and the bottom rack 38 on lower case plate 32.
  • the four case plates are each bolted to the input head 2% and the output head 26.
  • adjacent case plates are bolted to each other to form a rigid box housing suitable for accepting and transmitting the internal loads to an external mounting surface.
  • An input .rod 40 extends through the input head 20 and is supported therein through bushing 22.
  • a seal 24 isprovided to keep lubricants in and dirt out.
  • This input rod 40 is further guided by crosshead MBA which in turn is guided by the case plates 32, 3d and 36.
  • the input crosshead tiilA has two spaced extension plates 61 provided with rectangular openings which carry two slide blocks 62 with circular openings to house the input eccentric bearings 52.
  • the slide blocks 62 are slidably mounted in the openings in the extension plates 61 of the crosshead MA; these openings or slide slots are shown with slide axes perpendicular to the axis of the input rod 40, but these slots may be inclined or even curved to achieve greater versatility.
  • the input eccentric bearings 52 drive the input eccentrics 50 which are rigidly bolted to or integral with gear 54.
  • the eccentricity of the eccentrics 5th from the true centerline of the gear 54 may be varied from 0 to slightly more than the pitch radius of the gear, as one of the parameters which controls the force and kinematic characteristics of the system.
  • An output rod 70 extends through the output end plate 26 and is supported therein through bushing 28.
  • a seal 30 is provided to keep lubricants in and dirt out.
  • This output rod 70 is further guided by crosshead MA which in turn is guided by the case plates 32, 343 and 36.
  • the output crosshead 64A has spaced extension plates 65 each of which has a slot 65A to receive respective slide blocks 66 which house the output eccentric bearings 82.
  • the slide blocks 66 are slidably mounted in the slots 65A in the extension plates of crosshead 64A; these slots are shown with axes perpendicular to the axis of the output rod '70, but these slots may be inclined or even curved to achieve greater versatility as will be later explained in connection with FIG. 35.
  • the output eccentric bearings 82 are driven by the output eccentrics 80 which are rigidly bolted to or integral with the gear 54 and the input eccentrics 50.
  • the eccentricity of the eccentrics fit) from the true centerline of the gear 54 may be varied from O to slightly more than the pitch radius of the gear, as another of the pa rameters which controls the force and kinematic characteristics of the system.
  • phase angle between the drive wheel in the form of a gear 54 radial lines on which the input eccentrics 50 and the output eccentrics 80 are respectively located may again be varied to modify the force and kinematic characteristics of the system, even though this angle is shown as 0 in the drawings.
  • a rack 3b is rigidly bolted to the lower case plate 32 and is suitably formed and located to mesh with the gear 54-.
  • the gear teeth are conventional and not shown.
  • This rack will generally but not necessarily be slightly longer than one pitch circumference of the gear 54.
  • the gear 54 is provided with shoulders 55 which operate in bearings 58 mounted in guide block 5a.
  • This guide block 56 in turn is also guidedbetween the lower case plate 32 and the upper case plate 34 and maintains the pitch line of the gear 54 on the pitch line of the rack 38 during the rolling of the gear 54 along the rack 38.
  • This mechanism is defined to be operating in the slide mode because the eccentrics are connected to. their respective crossheads through sliding members.
  • the mechanism may also be built in one of two hybrid modes: in one the input eccentrics are link connected to the input crosshead and the output eccentrics are slide connected to the output. crosshead; in the other the input eccentrics are slide connected to their respective crosshead and the output eccentrics are link connected to the output crosshead.
  • a special but very important case occurs when the eccentricity of the input eccentrics 50 is 0, i.e., when the input eccentric bearings 52 are actually concentric with the gear 5d.
  • the input rod is directly connected to the gear guide block 56, eliminating the input crosshead, input eccentrics and the associated link or slide connection systems.
  • R Pitch radius of the. gear which is taken as l for all analyses R Distance from the center of the gear to the center of the output eccentrics R Distance from the center of the gear to the center of the input eccentrics n Phase angle between the gear radial line which contains the center of the input eccentrics and the gear radial line which contains the center of the output eccentrics. it is defined as positive if the input eccentric radial line is leading the output eccentric radial line in the direction of gear rotation.
  • FIG. 15 shows the position of the gear and eccentrics at the start of the motion. W, U and 0 are all equal to zero.
  • FIGS. 20 24 The qualitative sequence of movement in the link mode (the embodiment of FIGS. 11 to 7) is shown in FIGS. 20 24.
  • FIG. 20 shows the position of the gear and eccentrics at the start of motion. W, U, and are all equal to zero.
  • FIG. 21 represents the slide mode mechanism after the same amount of gear rotation.
  • the input W of the link mode is less than the W of the slide mode because of the slight increase in projected length of the input connector link.
  • the output U of the link mode is slightly greater than the U of the slide mode, again because of the slight increase in projected length of the output connector link.
  • FIGS. 25-29 The qualitative sequence in the slide mode, but with a phase angle u of 60 is shown in FIGS. 25-29.
  • the distance R is again equal to l, and the distance R is again equal to 0.25.
  • FIG. 25 shows the position of the gear and the eccentrics at the start of motion. W, U and 0 are all equal to zero.
  • the velocity and acceleration characteristics of the output are dependent not only on the mechanism but also on the velocity and acceleration characteristics of the input.
  • the input will be moved at a nomiinput velocity; and the term relative acceleration is defined for the purposes of this disclosure as the acceleration of the output again assuming a constant input velocity.
  • transfer functions are stated which describe the output velocity as a function of the input velocity, and other transfer functions are stated which describe the output acceleration as functions of the input velocity and input acceleration.
  • the output displacement characteristics relative to the input displacement are, of course, unaffected by either the velocity or acceleration of the input.
  • V (dU/dW) (l R cos 0/1 R cos 0)
  • Equations (3) and (4) express the relative velocity and acceleration of the output for a constant input velocity, with 6 as a calculating parameter. For every arbitrary value of 0, there is a corresponding value of U, W, (dU/dW), and (d UldW Therefore, for every value of W so obtained, there is a corresponding value of U, (dU/dW), and (d UldW It is with these relationships that we are concerned. In other words, 0 was used only as a mathematical convenience; and the output displacement, relative velocity, and relative acceleration will be shown in terms of the input position W.
  • the curves shown in FIGS. 36-41 represent the displacement, relative velocity, and. relative acceleration characteristics of the output plotted against input position for the slide mode, in phase, straight rack design.
  • the relative velocity and relative acceleration characteristics are predicated on the velocity of the input being constant.
  • FIGS. 36, 37 and 38 represent the characteristics of the output motion for the special case of R, l, i.e., the centerline of the output eccentric is located on the pitch line of the gear. Curves are drawn for various values of R It can be seen that a considerable change in the output motion characteristics can be accomplished by control of R alone. When R equals say 0.75 there 7 is an initial high acceleration which tapers off to a nearly zero acceleration (approximate constant velocity) over the center of the stroke which in turn is followed by a symmetrically high short deceleration. If R, were made still larger, these characteristics would be accentuated, i.e., shorter higher initial acceleration and symmetrical deceleration with a longer center interval of more nearly constant velocity.
  • the curves of FIGS. 39, 40 and 41 provide illustrative examples of the output motion characteristics when R, is not 1. As R, is made increasingly less than 1, the characteristics above described become less pronounced. The general effect of a change in R remains the same, but with milder results. When R, R the trivial result is obtained that the output motion exactly equals the input motion. If R, is made less than R a reversal of characteristics is found.
  • the initial relative velocity is no longer zero but is equal to the ratio (1 R,/l R
  • the velocity at the midpoint is a maximum if R, is greater than R, or a minimum if R, is less than R
  • the centerlines of the output eccentric and the input eccentric were located on the same radial line or diametral line of the gear, i.e., the phase angle was zero.
  • Still greater versatility is achieved by locating the centerline of the input eccentric on a different radial line of the gear than that on which the output eccentric is located. This angle is defined as the phase angle u and is positive if the input radial line is leading the output radial line in the direction the gear is rotating.
  • Equations (5) and (6) represent the relative velocity and relative acceleration for a slide mode, out of phase, straight rack system, with 6 again used as a calculating parameter.
  • the effect of the phase angle, u is illustrated in the representative curves of FIGS. 42, 43 and 44 in which the output displacement, output relative velocity, and output relative acceleration are plotted against the input displacement.
  • a single illustrative combination of R, and R is used which is R, l and R 0.50.
  • the parameter it therefore is a means through which a reasonable degree of nonsymmetry can be introduced into the output motion characteristics of the system.
  • the kinematic diagram for the link mode, in phase, straight rack system, R and R are as shown in FIG. 30.
  • the length of the input connector link is defined as a R that is, this link is (1 times longer than the radius R
  • the length of the output connector link is defined as a 11,.
  • the use of these definitions makes both oz, and a dimensionless numbers and the subsequent analyses will have a more general application.
  • the projected length of the input connector link on the line of action in its initial position is (az R RE) which equals R (a I).
  • equation (2) may be substituted into equation (2), but the resultant algebraic expression becomes so cumbersome that it is more convenient to accomplish the specific calculations byevaluating each derivative independently and then substituting their values into equation (2) to obtain the relative acceleration. This technique is even more: acceptable because it is ordinarily desired to evaluate the 0 derivatives in dependently in any case.
  • equation (2) may be rewritten:
  • FIG. 35 Another important and useful variation is a slide mode system in which the slots in the input and/or output crossheads are straight but not perpendicular to their direction of movement.
  • the kinematic diagram for the analysis of this system is shown in FIG. 35.
  • Another kinematic variation of importance is one in which the slots in the input crosshead, or output crosshead, or both, are curved or contoured as opposed to being straight, either inclined or perpendicular, as in the previous analyses.
  • Such contouring of the crosshead slots mechanically requires that the slide blocks be replaced by rollers to follow the non-uniform slot path.
  • Such contouring individually tailored to meet a specific requirement, creates a still greater flexibility between the input and output.
  • An example where this technique is of value is in a situation in which it is desired to generate an output dwell, at each end of the stroke, which is greater than any obtainable with any of the other systems.
  • the input and the output rods were colinear, and, in the straight rack design, the line of action passed through the center of the gear; in the curved rack design, the line of action passed near the average position of the output eccentric. It is also possible to have the input and output rods non-colinear, or to bring their lines of action closer to the racks so that the line of force transmittal is more nearly a straight line when the loads are the greatest, i.e., when the output eccentrics are nearest to the rack. Furthermore, the input and output rod need not be parallel to each other or to the plane of the rack.
  • the input and output rods were located on opposite sides of the travelling gear. It is also possible to locate the input and output rods on the same side of the gear, either side by side, one above the other, or in a coaxial arrangement, i.e., one of the two rods in a hollow tube, with the other rod slidably mounted therein.
  • gear eccentric assembly Another variation is the gear eccentric assembly.
  • the gear was symmetrically flanked by the input and output eccentrics respectively, which is a mechanically convenient arrangement.
  • a single output eccentric in the center of the assembly is flanked by the input eccentrics, the two gears and the gear guide bearings. This style is particularly attractive for the integral piston approach since it fits very conveniently into a circular section housing as opposed to a rectangular section housing or frame.
  • FIG. 48 Such a design is shown in section in FIG. 48 which is analogous to the sections in FIGS. 6 and 13.
  • the housing has connected to it two racks 92.
  • Two identical gears 94 are suitably formed and guided to mesh with the racks 92.
  • the gears 94 are bolted to or made integral with two input eccentrics 96 which in turn are bolted to or made integral with an output eccentric 98.
  • Each gear 94 supports a short shaft extension 104 concentric therewith which are guided in bearings 106 mounted in guide block 108.
  • the input crosshead is connected to the input eccentrics 96 through connector links 110 and bearings 112.
  • the output crosshead is connected to the output eccentric 98 through connector link and bearing 102.
  • This design shown in FIG. 48 employs the link mode; a similar design is usable with the slide mode or hybrid modes.
  • kinematic variations which may be usefully employed include multiple side-by-side gears having a point of mutual tangency which mesh with multiple corresponding side-by-side racks that overlap slightly at a crossover point where the gear tangency point becomes mutually tangent to both racks. This in effect creates a system which depends on one gear and rack system for a portion of the stroke and on the other gear and rack system for the remainder of the stroke. The same type of effect can be achieved by making the gear non-circular and having it mesh with a straight, curved, or non-circular rack.
  • additional locking capacity may be added to the system by utilizing the inherent transverse movement component of the output eccentric to engage an auxiliary locking pawl, pin, or equivalent between the output crosshead and the case.
  • the output links themselves may be designed to come to rest against a suitably formed heel block to provide additional lock capacity.
  • the input crosshead may be fitted closely to the case, transforming it into an effective piston as it moves through the case. If the case is nearly filled with a suitable lubricating oil, the crosshead will perform the function of a speed regulator, which may be made adjustable by adding a variable bypass.
  • the input rod may be eliminated completely, and the input crosshead used as a piston driven by fluid introduced through suitable ports at each end of the enclosed case.
  • Electrical limit switches may be added to be operated by the input system as a means to determine when the output is at one end of the stroke or the other. This arrangement is advantageous because of the much greater resolution this makes possible.
  • One set of points of particular interest are those at which the output relative velocity is zero. At such a point (dU/dW) 0. Therefore, [(dU/d6)/(dW/d0)] 0, and (dU/dO) must equal if (d W/dfl) is finite.
  • Each point of zero output velocity is therefore a function only of the output mechanism geometry. The input mechanism geometry will effect only the rate at which the output velocity passes through the zero point, but will not effect the position of this zero point.
  • the relative velocity curve has a finite slope (equal to the acceleration) and in passing through zero must change sign. This means that the displacement curve reaches either a maximum or a minimum (not a point of inflection) and that an overshoot of the input beyond this point causes reversal of the output.
  • the relative velocity curve has 0 slope and reaches a maximum or minimum at a tangency point to the hor izontal axis. At this point, the displacement curve has a horizontal point of inflection. Therefore, any overtravel of the input causes the output to. move in the same direction it had been moving, i.e., there is no reversal.
  • the dwell of the output is a maximum as described above.
  • a mechanical system for transferring and modifying motion from a lineal input to a lineal output which comprises:
  • lineal input means connected to a first off-center point on said wheel to drive said wheel in nonuniform rotation along said path
  • v e. lineal output means connected to a second offcenter point of said wheel wherein rotation of said wheel adds vectorially, the motion of said wheel along said first means and the distance of said second off-center point from the center of said wheel in the direction of the input motion.
  • said lineal input means comprises an input rod, a first pair of spaced links pivotally connected at one end to said rod and having holes at the other end, .a round projection on each side of said wheel interfitting with a hole in each of said links to have a rotating fit
  • said lineal output means comprises an output rod, 21 second pair of spaced links pivotally connected at one end to said output rod and having holes at the other end, a second round projection on each of said first round projections positioned at the said offcenter point relative to said drive wheel, said second which comprises: a. a housing defining an elongate chamber, b. an input rod movable into and out of one 7 end of said housing and an output rod movable into and out of the other end of said housing,
  • each crosshead connected to each of said rods, each crosshead being slidable in said housing and each having a pair of parallel plate extensions extending toward each other and spaced to interfit with each other, each of said plate extensions having a slot extending at an angle to the general direction of the said housing chamber,
  • a mechanical system for transferring motion which comprises:
  • a housing defining an elongate chamber
  • each crosshead connected to each of said rods, each crosshead being slidable in said housing and each having a pair of parallel plate extensions extending toward each other and spaced to interfit with each other, each of said plate extensions having a slot extending at an angle to the general direction of the said housing chamber,
  • an intermediate means connecting said input member to said output member comprising:
  • a motion transforming system as defined in claim 9 in which said means connecting said output member to said output shaft and said input member to said input shaft comprise respective link means pivoted at one point to said respective shafts and at another point to said respective members.
  • an intermediate means connecting said input member to said output member comprising:
  • said means connecting said output member to said output shaft and said input member to said input shaft comprising follower means movable in a confined path generally transverse of said lineal motion in said respective input and output members, and
  • each said follower means means in each said follower means to receive, respectively, in rotatable relation, said input and output shafts.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
US00185273A 1971-09-30 1971-09-30 Motion and force transforming mechanism Expired - Lifetime US3777580A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US18527371A 1971-09-30 1971-09-30

Publications (1)

Publication Number Publication Date
US3777580A true US3777580A (en) 1973-12-11

Family

ID=22680316

Family Applications (1)

Application Number Title Priority Date Filing Date
US00185273A Expired - Lifetime US3777580A (en) 1971-09-30 1971-09-30 Motion and force transforming mechanism

Country Status (8)

Country Link
US (1) US3777580A (de)
JP (2) JPS4842255A (de)
AU (1) AU464491B2 (de)
CA (1) CA966690A (de)
FR (1) FR2155453A5 (de)
GB (1) GB1401789A (de)
IT (1) IT966122B (de)
SE (1) SE384723B (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4284605A (en) * 1980-05-14 1981-08-18 Ferrofluidics Corporation Linear drive shaft seal
US4332176A (en) * 1978-01-12 1982-06-01 Expert Automation, Inc. Mechanical motion control apparatus
US4360325A (en) * 1981-02-27 1982-11-23 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Gas-to-hydraulic power converter
US4584893A (en) * 1982-03-17 1986-04-29 Harcross Engineering (Barnstaple) Ltd. Lubrication of rack and pinion apparatus
US4593843A (en) * 1982-08-24 1986-06-10 Saravis Lawrence M Surgical stapler for implanting sutures
US4899606A (en) * 1988-09-19 1990-02-13 Harris Marion K Apparatus for assembling parts and discharging assembled parts
US20110232405A1 (en) * 2010-03-24 2011-09-29 Cameron International Corporation Compact-actuator gear set
US20120246900A1 (en) * 2010-09-29 2012-10-04 Shimmel Jeffrey T Portable equipment system mount

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US444016A (en) * 1891-01-06 Mechanical movement
US455248A (en) * 1891-06-30 Mechanical movement
US1751646A (en) * 1926-01-07 1930-03-25 Henry W Nieman Mechanical movement
US2047061A (en) * 1931-10-10 1936-07-07 Packard Motor Car Co Valve actuating mechanism
US2440457A (en) * 1944-05-22 1948-04-27 Milwaukee Electric Tool Corp Pneumatic tool

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US444016A (en) * 1891-01-06 Mechanical movement
US455248A (en) * 1891-06-30 Mechanical movement
US1751646A (en) * 1926-01-07 1930-03-25 Henry W Nieman Mechanical movement
US2047061A (en) * 1931-10-10 1936-07-07 Packard Motor Car Co Valve actuating mechanism
US2440457A (en) * 1944-05-22 1948-04-27 Milwaukee Electric Tool Corp Pneumatic tool

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4332176A (en) * 1978-01-12 1982-06-01 Expert Automation, Inc. Mechanical motion control apparatus
US4284605A (en) * 1980-05-14 1981-08-18 Ferrofluidics Corporation Linear drive shaft seal
US4360325A (en) * 1981-02-27 1982-11-23 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Gas-to-hydraulic power converter
US4584893A (en) * 1982-03-17 1986-04-29 Harcross Engineering (Barnstaple) Ltd. Lubrication of rack and pinion apparatus
US4593843A (en) * 1982-08-24 1986-06-10 Saravis Lawrence M Surgical stapler for implanting sutures
US4899606A (en) * 1988-09-19 1990-02-13 Harris Marion K Apparatus for assembling parts and discharging assembled parts
US20110232405A1 (en) * 2010-03-24 2011-09-29 Cameron International Corporation Compact-actuator gear set
KR20130004578A (ko) * 2010-03-24 2013-01-11 카메론 인터내셔널 코포레이션 소형 액츄에이터 기어 세트
CN106931116A (zh) * 2010-03-24 2017-07-07 卡梅伦国际有限公司 包括齿轮箱组件的系统
US9909683B2 (en) * 2010-03-24 2018-03-06 Cameron International Corporation Compact-actuator gear set
US20120246900A1 (en) * 2010-09-29 2012-10-04 Shimmel Jeffrey T Portable equipment system mount
US9423069B2 (en) 2010-09-29 2016-08-23 The United States Of America As Represented By The Secretary Of The Navy Portable equipment system mount
US9752721B2 (en) * 2010-09-29 2017-09-05 The United States Of America As Represented By The Secretary Of The Navy Portable equipment system mount

Also Published As

Publication number Publication date
DE2248064B2 (de) 1976-01-29
FR2155453A5 (de) 1973-05-18
AU464491B2 (en) 1975-08-28
JPS4842255A (de) 1973-06-20
SE384723B (sv) 1976-05-17
GB1401789A (en) 1975-07-30
DE2248064A1 (de) 1973-04-05
JPS52168174U (de) 1977-12-20
AU4681472A (en) 1974-03-28
CA966690A (en) 1975-04-29
JPS5726999Y2 (de) 1982-06-11
IT966122B (it) 1974-02-11

Similar Documents

Publication Publication Date Title
US5954615A (en) Speed converter
US3777580A (en) Motion and force transforming mechanism
US5456159A (en) Motion converter with pinion sector/rack interface
US2943508A (en) Strain wave gearing-linear motion
US4713985A (en) Transmission apparatus
US3730014A (en) Rotary indexing mechanism
US3459056A (en) Constant torque transmission
US2112934A (en) Swash plate drive system and the like
US2931248A (en) Strain wave gearing-strain inducer species
US3592067A (en) Device for converting between linear and circular movement
US3859862A (en) Cyclicly repetitive motion generating system
US4955243A (en) Motion transforming apparatus
US4726240A (en) Transfer mechanism and drive with straight line lift and lower
US3753386A (en) Valve actuator
US4070855A (en) Constant force motor
US4836040A (en) Differential rotary-to-rotary cam system to achieve long dwell periods with continuous rotary input
US3563101A (en) Intermittent drive device
US4244233A (en) Reciprocating indexing mechanism
US3344715A (en) Hydraulic motors
CA1047279A (en) Reciprocating indexing mechanism
GB2131516A (en) Rotary motion cam system
US4770081A (en) Servomechanism with idle gear feedback
US5119686A (en) Constant breadth cambox
US2889783A (en) Pump or motor having four cylinders arranged in one plane
CA1271055A (en) Reciprocating long dwell mechanism